JPH04331816A - Bush for oil film bearing - Google Patents
Bush for oil film bearingInfo
- Publication number
- JPH04331816A JPH04331816A JP3021364A JP2136491A JPH04331816A JP H04331816 A JPH04331816 A JP H04331816A JP 3021364 A JP3021364 A JP 3021364A JP 2136491 A JP2136491 A JP 2136491A JP H04331816 A JPH04331816 A JP H04331816A
- Authority
- JP
- Japan
- Prior art keywords
- bushing
- bearing
- bearing surface
- recess
- axis
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000005096 rolling process Methods 0.000 claims abstract description 8
- 230000002093 peripheral effect Effects 0.000 claims description 7
- 239000000314 lubricant Substances 0.000 claims description 6
- 239000003921 oil Substances 0.000 claims 4
- 230000001050 lubricating effect Effects 0.000 claims 2
- 239000010687 lubricating oil Substances 0.000 claims 2
- 230000002706 hydrostatic effect Effects 0.000 abstract description 11
- 230000003628 erosive effect Effects 0.000 abstract description 3
- 239000002184 metal Substances 0.000 description 3
- 238000006073 displacement reaction Methods 0.000 description 2
- 238000009826 distribution Methods 0.000 description 2
- 230000002411 adverse Effects 0.000 description 1
- 230000000712 assembly Effects 0.000 description 1
- 238000000429 assembly Methods 0.000 description 1
- 238000011109 contamination Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 239000000498 cooling water Substances 0.000 description 1
- 238000005336 cracking Methods 0.000 description 1
- 238000005520 cutting process Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000008030 elimination Effects 0.000 description 1
- 238000003379 elimination reaction Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C32/00—Bearings not otherwise provided for
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
- F16C32/0629—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion
- F16C32/064—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion the liquid being supplied under pressure
- F16C32/0651—Details of the bearing area per se
- F16C32/0659—Details of the bearing area per se of pockets or grooves
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B31/00—Rolling stand structures; Mounting, adjusting, or interchanging rolls, roll mountings, or stand frames
- B21B31/07—Adaptation of roll neck bearings
- B21B31/074—Oil film bearings, e.g. "Morgoil" bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/10—Construction relative to lubrication
- F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
- F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
- F16C33/1075—Wedges, e.g. ramps or lobes, for generating pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2322/00—Apparatus used in shaping articles
- F16C2322/12—Rolling apparatus, e.g. rolling stands, rolls
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Oil, Petroleum & Natural Gas (AREA)
- Sliding-Contact Bearings (AREA)
- Compressor (AREA)
- Magnetic Bearings And Hydrostatic Bearings (AREA)
Abstract
Description
【0001】0001
【産業上の利用分野】本発明は、圧延機のロールネック
のジャーナル面を回転できるように支持するのに用いる
形式の油膜軸受の改良に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement in an oil film bearing of the type used to rotatably support the journal surface of a roll neck of a rolling mill.
【0002】0002
【従来の技術】油膜軸受をもつ代表的圧延機の使用にお
いて、多少略示的に図1および図2に示したように、ロ
ール10はネック部12を有する。図示のように、この
ネック部12は先細りでもよく、または円柱にもできる
。スリーブ14は上記ネック部12上に嵌合し、1個ま
たは2個以上のキー13により回転できるように固定さ
れる。上記スリーブの外部は上記ロールネックのジャー
ナル面16を形成する。ブシュ18は、上記ジャーナル
面16を取り囲み、かつ回転できるように支持する内部
軸受面20を有する。上記ブシュはチョーク22によっ
て囲まれ、かつチョーク22内に固定される。上記チョ
ークはロールハウジング(図示せず)内に支持されるよ
うになっており、そして端板24およびカバー26によ
り外端部において密閉される。シール組立28は、上記
ロールと上記チョーク22の内端部との間に設けられる
。上記シール組立は上記軸受内に潤滑油を保持する作用
をすると同時に、冷却水、ミルスケール、その他による
潤滑油および内部軸受構成要素の汚染を予防する。BACKGROUND OF THE INVENTION In the use of a typical rolling mill with oil film bearings, a roll 10 has a neck 12, as shown somewhat schematically in FIGS. The neck 12 may be tapered, as shown, or it may be cylindrical. A sleeve 14 fits over the neck 12 and is rotatably secured by one or more keys 13. The exterior of the sleeve forms the journal surface 16 of the roll neck. Bushing 18 has an internal bearing surface 20 that surrounds and rotatably supports journal surface 16 . The bushing is surrounded by and fixed within the choke 22. The choke is adapted to be supported within a roll housing (not shown) and is sealed at the outer end by an end plate 24 and cover 26. A seal assembly 28 is provided between the roll and the inner end of the choke 22. The seal assembly functions to retain lubricant within the bearing while preventing contamination of the lubricant and internal bearing components by cooling water, mill scale, and the like.
【0003】上記圧延機の正常運転中、流体力学的全力
運転の適切な速度で上記ロールが図2の矢印で示した方
向に回転している時には、油の連続流れが、上記チョー
クの通路29、上記ブシュの送り孔30および上記軸受
面20の開け広げ部32を経て送られる。ここから上記
油は軸受面20と回転しているジャーナル面16との間
に入り、軸受荷重領域“Z”において、流体力学的に圧
力維持される油膜34を形成する。上記荷重領域は、上
記ロールに加えれれる荷重“L”の領域とは反対側に位
置する。During normal operation of the rolling mill, when the rolls are rotating in the direction indicated by the arrows in FIG. , through the feed hole 30 of the bush and the widened portion 32 of the bearing surface 20. From here, the oil enters between the bearing surface 20 and the rotating journal surface 16 and forms a hydrodynamically pressure-maintained oil film 34 in the bearing load zone "Z". The load area is located on the opposite side from the area of load "L" applied to the roll.
【0004】上記油は最後に、ジャーナル面16と軸受
面20との間から軸線方向に漏れ出て、内側油だめ36
および外側油だめ38内に収容される。ここから上記油
は、上記軸受に帰されるに先だち、フィルタ、冷却装置
その他(図示せず)を経て再循環される。The oil finally leaks out in the axial direction from between the journal surface 16 and the bearing surface 20 and enters the inner oil sump 36.
and is housed within the outer oil sump 38. From there the oil is recirculated via filters, cooling devices, etc. (not shown) before being returned to the bearings.
【0005】もしも、ジャーナル面16の回転速度、上
記油の荷重Lおよび粘度が、すべて設計限界内にあれば
、上記軸受荷重領域“Z”で流体力学的に圧力維持され
る適切な油膜34のために、軸受は満足に作用を継続す
る。しかし、万一これらのパラメータの中の1つが下方
設計限界以下に低下したならば、上記流体力学的圧力維
持油膜は劣化または崩壊のおそれがあり、ジャーナル面
16と軸受面20との間に金属対金属の接触を生じさせ
る。万一これが起これば、その結果生じる摩擦が急速に
軸受の破損を起こす。If the rotational speed of the journal surface 16, the load L and the viscosity of the oil are all within the design limits, an appropriate oil film 34 is formed to maintain pressure hydrodynamically in the bearing load region "Z". Therefore, the bearing continues to function satisfactorily. However, if one of these parameters were to drop below the lower design limit, the hydrodynamic pressure-maintaining oil film could deteriorate or collapse, leaving no metal between the journal face 16 and the bearing face 20. Creates metal-to-metal contact. Should this occur, the resulting friction will rapidly cause bearing failure.
【0006】従って、圧延機始動時における回転速度ゼ
ロから、満足な流体力学的運転のための下方設計限界ま
で、上記荷重領域Zにおける油膜34は、上記記載の流
体力学的技術以外の手段により作り出し、かつ維持しな
ければならない。この目的のために、そしてさらに図3
ないし図5に関連して、従来技術の型にはまった軸受組
立においては、荷重領域Zの軸受面20内に多数の静油
圧凹部40を備えていることが周知である。上記凹部4
0は容積式定容高圧油ポンプ44に、通路42すなわち
導管装置の回路網によって相互連通される。[0006] Therefore, from zero rotational speed at rolling mill start-up to the lower design limit for satisfactory hydrodynamic operation, the oil film 34 in the load region Z can be created by means other than the hydrodynamic techniques described above. , and must be maintained. For this purpose, and furthermore, Figure 3
With reference to FIGS. 5-5, it is known in prior art conventional bearing assemblies to provide a number of hydrostatic recesses 40 in the bearing surface 20 in the load area Z. Said recess 4
0 is interconnected with a positive displacement, constant volume, high pressure oil pump 44 by a network of passageways 42 or conduit systems.
【0007】ブシュの内側から半径方向に見た場合、従
来技術設計の上記凹部40は、形状が一般に長方形であ
る。これら凹部の両端部は46におけるように端を薄く
そがれ、それに反し底部48と側壁50とは相互に垂直
となり、従って鋭い底部コーナ52を形成する。上記側
壁50は軸受面20に垂直で、それによって鋭い上縁5
3を形成する。When viewed radially from the inside of the bushing, the recess 40 of prior art designs is generally rectangular in shape. The ends of these recesses are tapered as at 46, whereas the bottom 48 and side walls 50 are mutually perpendicular, thus forming a sharp bottom corner 52. Said side wall 50 is perpendicular to the bearing surface 20 so that a sharp upper edge 5
form 3.
【0008】この形式の配置のために、流体静力学的に
油膜34を作成するために上記油が各凹部40から出て
くる時に、油は極めて高い抵抗に出会い、このようにし
て油が上記の鋭い上縁53と軸受面20との間を軸線方
向に強制供給される時には著しい圧力降下を経験する。
最終結果として、上記油膜34内に所定油圧を維持する
ためには、実質的にさらに高い油圧を上記凹部40内に
維持しなければならないということである。この結果は
次に、上記ポンプ44が過度に運転しなければならず、
そして全潤滑系は高圧で作動するように設計しなければ
ならないことを意味する。Because of this type of arrangement, the oil encounters extremely high resistance as it emerges from each recess 40 to hydrostatically create an oil film 34, thus causing the oil to When forced axially between the sharp upper edge 53 of the bearing surface 20 and the bearing surface 20, a significant pressure drop is experienced. The end result is that in order to maintain a predetermined oil pressure in the oil film 34, a substantially higher oil pressure must be maintained in the recess 40. The result of this is that the pump 44 must then run excessively;
This means that the entire lubrication system must be designed to operate at high pressures.
【0009】また、各凹部40の周囲から出てくる油は
、上記鋭い上縁53を軸線方向に通過して出る油が出会
う抵抗と比較して、凹部の薄くそいだ端部46において
は著しく少ない抵抗に出会うことが理解されよう。この
ことは軸流を犠牲にして円周方向流を促進させるもので
、上記軸流は荷重領域全体にわたり油圧界の分布に不利
な影響を及ぼす。油圧界は荷重領域において荷重を支え
る。[0009] Also, the oil coming out from around each recess 40 faces significantly less resistance at the thinner end 46 of the recess than the resistance encountered by the oil passing axially through the sharp upper edge 53. It will be appreciated that less resistance will be encountered. This promotes circumferential flow at the expense of axial flow, which adversely affects the distribution of the hydraulic field over the load area. The hydraulic field supports the load in the load area.
【0010】上記従来設計の他の欠点は、上記底部コー
ナ52における高度の応力集中を含み、応力集中はき裂
を生じて軸受の破損を起こすおそれがある。また、上記
鋭い上縁53における流れ領域の急激な変化は、比較的
高い流体速度を生じ、次に金属エロージョンを速める。Other drawbacks of the prior art design include a high degree of stress concentration at the bottom corner 52, which can cause cracking and failure of the bearing. Also, the abrupt change in flow field at the sharp upper edge 53 results in relatively high fluid velocities, which in turn accelerates metal erosion.
【0011】[0011]
【発明が解決しようとする課題】本発明の目的は、従来
技術に関連する問題点を、避けるかまたは非常に少ない
実質的に最少限度に少なくする、新規で改良された静油
圧凹部の構成を備えたブシュを提供することにある。SUMMARY OF THE INVENTION It is an object of the present invention to provide a new and improved hydrostatic recess configuration which avoids or reduces to a very small, substantially minimum, the problems associated with the prior art. The objective is to provide a bushing with the following features.
【0012】0012
【課題を解決するための手段】本発明によれば、静油圧
凹部を具備する改良されたブシュが設けられ、上記静油
圧凹部は上記ブシュの内側から半径方向に見た場合、事
実上楕円形の端部を薄くそいだ周辺縁を有している。上
記凹部の長軸はブシュ軸線に対し横方向に伸び出し、こ
れに反して上記凹部の短軸は上記ブシュ軸線に対し平行
に伸び出ている。各凹部の深さは均一ではなくて、その
薄いそいだ周辺縁から、凹部の長軸と短軸との交点にお
ける最大値まで漸次増加する。SUMMARY OF THE INVENTION According to the present invention, an improved bushing is provided having a hydrostatic recess, said hydrostatic recess having a substantially elliptical shape when viewed radially from the inside of said bushing. It has a peripheral edge with a thinly rounded edge. The major axis of the recess extends transversely to the bushing axis, whereas the minor axis of the recess extends parallel to the bushing axis. The depth of each recess is not uniform, but increases gradually from its thin peripheral edge to a maximum at the intersection of the long and short axes of the recess.
【0013】本発明の各静油圧凹部は、上記ブシュの内
部軸受面と共に回転する2重曲線面の交差により作られ
る長球面の一部分を形成するものとして考えられる。回
転の2重曲線面は一般に、上記ブシュの軸受面で取り囲
まれる回転軸線を有し、かつブシュ縦軸線に対して平行
に伸び出る円環面である。Each hydrostatic recess of the invention can be thought of as forming part of a prolate spherical surface created by the intersection of a double curved surface that rotates with the internal bearing surface of the bushing. The double curved surface of rotation is generally a toric surface having an axis of rotation surrounded by the bearing surface of the bushing and extending parallel to the longitudinal axis of the bushing.
【0014】本発明の一実施例を、添付図面と関連して
単に一例として次に記載する。An embodiment of the invention will now be described, by way of example only, in conjunction with the accompanying drawings, in which:
【0015】[0015]
【実施例】図6ないし図14について以下説明すると、
本発明によるブシュが60で示される。上記ブシュは、
軸受中心の両側に対称的に配置された一対の静油圧凹部
64を備えた円筒形の内部軸受面62を有する。[Example] Figs. 6 to 14 will be explained below.
A bushing according to the invention is shown at 60. The above bushing is
It has a cylindrical internal bearing surface 62 with a pair of hydrostatic recesses 64 symmetrically positioned on either side of the bearing center.
【0016】各凹部64は、ブシュの内側から半径方向
に見た場合、連続的な端を薄くそいだ縁66で取り囲ま
れ(図6に示されるように)、ブシュ縦軸線Aに対し横
方向に伸び出す長軸X、および縦軸線Aに対し平行に伸
び出す短軸Yを具備した事実上楕円形状である。Each recess 64 is surrounded by a continuous edge 66 when viewed radially from inside the bushing (as shown in FIG. 6) and transverse to the bushing longitudinal axis A. It is substantially elliptical in shape, with a major axis X extending parallel to the longitudinal axis A and a minor axis Y extending parallel to the longitudinal axis A.
【0017】図11および図12に示されるように、各
凹部64は円環面68と内部軸受面62との交差により
形成される。上記円環面68は軸線Bの周りに平面曲線
70の回転により作られる。上記曲線70は事実上、半
径Rx を有する切断縁外形を構成する。上記円環面6
8は半径Rx≠かつ上記ブシュ縦軸線Aに平行である。As shown in FIGS. 11 and 12, each recess 64 is formed by the intersection of an annular surface 68 and an internal bearing surface 62. As shown in FIGS. The toric surface 68 is created by rotating the planar curve 70 around the axis B. The curve 70 effectively constitutes a cutting edge profile with radius Rx. Said toric surface 6
8 is radius Rx≠ and parallel to the bushing longitudinal axis A.
【0018】図7および図8に関連して、上記長軸Xに
垂直にとった連続断面は、おのおの半径Rxモ心からそ
の両端部に向かって進むにつれて、上記各セグメントの
深さdと幅wは漸次小さくなる。同様にして、図9およ
び図10に関連して、上記短軸Yに垂直にとった連続断
面は、半径Rxb 中心からその両端部に向かって進む
につれて、連続部分の深さdと長さlは漸次小さくなる
。
従って各凹部64は長球面の一部分を形成するというこ
とになる。7 and 8, a continuous cross section taken perpendicular to the long axis X shows the depth d and width w of each segment as it progresses from the center of the radius R becomes gradually smaller. Similarly, in relation to FIGS. 9 and 10, a continuous section taken perpendicular to the short axis Y has a radius Rxb, and as it progresses from the center toward both ends, the depth d and length l of the continuous section becomes gradually smaller. Therefore, each recess 64 forms a part of a prolate sphere.
【0019】[0019]
【発明の効果】図13および図14は、油膜軸受組立内
に取り付けられた本発明のブシュを示す。従来技術の凹
部40の鋭いコーナ側縁の代りに、本発明の静油圧凹部
64の連続的に端を薄くそいだ周縁66は、著しく少な
い圧力降下を伴いながら、軸線方向に出る油の円滑、か
つ低速度の流れを調節する。従って上記凹部64内の低
い油圧が、流体静力学的に圧力を維持する油膜34内の
所定圧力を維持するために要求される。油の速度が低い
ことは、凹部周縁66のエロージョンを減少させ、さら
に鋭いコーナの削除は、潜在的に損害を与える応力集中
を著しく減少させる。FIGS. 13 and 14 illustrate the bushing of the present invention installed within an oil film bearing assembly. Instead of the sharp corner edges of the prior art recess 40, the continuously edged periphery 66 of the hydrostatic recess 64 of the present invention provides smooth and smooth oil exit in the axial direction with significantly less pressure drop. and regulate low velocity flow. Therefore, a low oil pressure in the recess 64 is required to maintain a predetermined pressure in the oil film 34, which maintains the pressure hydrostatically. The low oil velocity reduces erosion of the recess periphery 66, and the elimination of sharp corners significantly reduces potentially damaging stress concentrations.
【0020】そしてまた、上記凹部の両端部における減
少した幅wから起こる周辺流路の漸減は(図7と図8の
比較)、周辺流れに抵抗して、軸流を一段と助長し、従
って上記荷重領域全体にわたり油の分布を一層良好にす
る。[0020] Also, the gradual reduction of the peripheral flow path resulting from the reduced width w at both ends of the recess (compare FIGS. 7 and 8) resists the peripheral flow and further promotes the axial flow, thus Better distribution of oil over the entire load area.
【図1】従来形設計のブシュを含む油膜軸受組立を通る
縦断面である。1 is a longitudinal section through an oil film bearing assembly including a bushing of conventional design; FIG.
【図2】図1の線2−2による拡大断面図である。FIG. 2 is an enlarged cross-sectional view taken along line 2-2 in FIG. 1;
【図3】図2の線3−3による断面図である。FIG. 3 is a cross-sectional view taken along line 3-3 of FIG. 2;
【図4】図2に示した断面図の一部の拡大図である。FIG. 4 is an enlarged view of a portion of the cross-sectional view shown in FIG. 2;
【図5】図4の線5−5による断面図である。FIG. 5 is a cross-sectional view taken along line 5-5 of FIG. 4;
【図6】図3に類似するが、本発明のブシュの拡大図で
ある。FIG. 6 is similar to FIG. 3 but in an enlarged view of the bushing of the invention;
【図7】図6の線7−7による著しく拡大した断面図で
ある。FIG. 7 is a greatly enlarged cross-sectional view taken along line 7-7 of FIG. 6;
【図8】図6の線8−8による著しく拡大した断面図で
ある。FIG. 8 is a greatly enlarged cross-sectional view taken along line 8-8 of FIG. 6;
【図9】図7の線9−9による断面図である。9 is a cross-sectional view taken along line 9-9 of FIG. 7. FIG.
【図10】図7の線10−10による断面図である。10 is a cross-sectional view taken along line 10-10 of FIG. 7. FIG.
【図11】本発明の静油圧凹部がブシュの内部軸受面で
如何に展開しているかを示す略示図である。FIG. 11 is a schematic diagram showing how the hydrostatic recess of the invention is developed on the internal bearing surface of the bushing;
【図12】図11の線12−12による拡大図である。FIG. 12 is an enlarged view taken along line 12-12 of FIG. 11;
【図13】軸受組立内に取り付けられた本発明のブシュ
を示す図4に類似の図である。13 is a view similar to FIG. 4 showing the bushing of the present invention installed within a bearing assembly; FIG.
【図14】図13の線14−14による断面図である。14 is a cross-sectional view taken along line 14-14 of FIG. 13. FIG.
10 ロール 12 ネック部 13 キー 14 スリーブ 16 ジャーナル面 18 ブシュ 20 内部軸受面 22 チョーク 26 カバー 28 シール組立 29 通路 30 送り孔 32 開け広げ部 34 油膜 36 内側油だめ 38 外側油だめ 40 静油圧凹部 42 通路すなわち導管装置 44 容積式定容高圧油ポンプ 46 薄くそいだ端部 48 底部 50 側壁 52 鋭い底部コーナ 53 鋭い上縁 60 ブシュ 62 内部軸受面 64 静油圧凹部 66 連続的な端を薄くそいだ周縁 68 円環面 70 平面曲線 A ブシュ縦軸線 B 軸線 L ロールに加わる荷重 X 長軸 Y 短軸 Z 軸受荷重領域 d 深さ l 長さ w 幅 10 rolls 12 Neck part 13 key 14 Sleeve 16 Journal surface 18 Bush 20 Internal bearing surface 22 Chalk 26 Cover 28 Seal assembly 29 Passage 30 Spread hole 32 Opening part 34 Oil slick 36 Inner oil sump 38 Outside oil sump 40 Hydrostatic recess 42 Passage or conduit device 44 Positive displacement constant volume high pressure oil pump 46 Thin edge 48 Bottom 50 Side wall 52 Sharp bottom corner 53 Sharp upper edge 60 Bush 62 Internal bearing surface 64 Hydrostatic recess 66. Continuous edge with a thin edge 68 Toric surface 70 Plane curve A Bush vertical axis line B Axis line Load applied to L roll X Long axis Y short axis Z Bearing load area d Depth l Length w Width
Claims (10)
を回転できるように支持するために用いる形式の油膜軸
受組立に使用するブシュであって、該ブシュが、上記ジ
ャーナル面を取り囲むようになっている円筒形の内部軸
受面を有する壁と、該壁を通って伸び出し、加圧下の液
体潤滑剤を上記軸受面と上記ジャーナル面との間の荷重
領域へ送る導管装置と、該導管装置に連通し、上記の送
られた加圧下の潤滑剤を受け入れ、かつ上記ジャーナル
面を上記軸受面から分離する潤滑薄膜の形式で上記潤滑
剤を上記荷重領域内に分配する上記軸受面内の少なくと
も1個の凹部とを備え、該凹部が上記軸受面と共に回転
する2重曲線面の交差により形成されることを特徴とす
る油膜軸受用ブシュ。1. A bushing for use in an oil film bearing assembly of a type used for rotatably supporting a journal surface of a roll neck of a rolling mill, the bushing surrounding the journal surface. a wall having a cylindrical internal bearing surface; and a conduit device extending through the wall and communicating with the conduit device for conveying liquid lubricant under pressure to a load area between the bearing surface and the journal surface. and at least one of said bearing surfaces receiving said delivered lubricant under pressure and distributing said lubricant within said load area in the form of a lubricating film separating said journal surface from said bearing surface. A bushing for an oil film bearing, characterized in that the recess is formed by the intersection of double curved surfaces that rotate together with the bearing surface.
とを特徴とする請求項1のブシュ。2. The bushing according to claim 1, wherein the rotation double curved surface is a toric surface.
シュの縦軸線に平行で、かつ上記軸受面で取り囲まれる
ことを特徴とする請求項2のブシュ。3. The bushing according to claim 2, wherein the axis of rotation of said double curved surface is parallel to the longitudinal axis of said bushing and is surrounded by said bearing surface.
記軸受面の半径より小さいことを特徴とする請求項3の
ブシュ。4. The bushing according to claim 3, wherein a radius of rotation of said two-axis rotational curved surface is smaller than a radius of said bearing surface.
ことを特徴とする請求項1のブシュ。5. The bushing of claim 1, wherein said recess forms a portion of a prolate spherical surface.
ることを特徴とする請求項1のブシュ。6. The bushing of claim 1, wherein said recess has a substantially oval peripheral edge.
に伸び出す長軸、および上記ブシュ縦軸線に平行な方向
に伸び出す短軸を有することを特徴とする請求項6のブ
シュ。7. The bushing according to claim 6, wherein the recess has a long axis extending in a direction perpendicular to the longitudinal axis of the bushing and a short axis extending in a direction parallel to the longitudinal axis of the bushing.
る断面が、円のセグメントを形成することを特徴とする
請求項7のブシュ。8. Bushing according to claim 7, characterized in that a cross section through said recess in a direction perpendicular to said longitudinal axis forms a segment of a circle.
る断面が、円の部分を形成することを特徴とする請求項
7または請求項8のいずれか1項のブシュ。9. Bushing according to claim 7, characterized in that a cross section passing through the recess in a direction perpendicular to the minor axis forms a circular section.
面を回転できるように支持するために用いる形式の油膜
軸受組立に使用するブシュであって、該ブシュが、上記
ジャーナル面を取り囲むようになっている円筒形の内部
軸受面を有する壁と、該壁を通って伸び出し、加圧下の
液体潤滑剤を上記軸受面と上記ジャーナル面との間の荷
重領域へ送る導管装置と、該導管装置に連通し、上記の
送られた潤滑剤を受け入れ、かつ上記ジャーナル面を上
記軸受面から分離する潤滑薄膜の形式で上記潤滑剤を上
記荷重領域内に分配する、上記軸受面内の複数凹部とを
備え、該凹部が上記荷重領域の中心に対して対称的に配
置され、上記凹部のおのおのが、ブシュ縦軸線に垂直な
方向に伸び出す長軸、および上記ブシュ縦軸線に平行な
方向に伸び出す短軸を有し、上記凹部のおのおのが、事
実上楕円形周辺縁、および該周辺縁から、上記長軸と短
軸とが交差する最大深さまで漸次増加する不均一深さを
有することを特徴とする油膜軸受用ブシュ。10. A bushing for use in an oil film bearing assembly of a type used for rotatably supporting a journal surface of a roll neck of a rolling mill, the bushing surrounding the journal surface. a wall having a cylindrical internal bearing surface; and a conduit device extending through the wall and communicating with the conduit device for conveying liquid lubricant under pressure to a load area between the bearing surface and the journal surface. a plurality of recesses in said bearing surface for receiving said delivered lubricant and distributing said lubricant within said load area in the form of a lubricating film separating said journal surface from said bearing surface; , the recesses are arranged symmetrically with respect to the center of the load area, and each of the recesses has a long axis extending in a direction perpendicular to the longitudinal axis of the bushing and a short axis extending in a direction parallel to the longitudinal axis of the bushing. having an axis, each of said recesses having a substantially elliptical peripheral edge and a non-uniform depth increasing progressively from said peripheral edge to a maximum depth where said major and minor axes intersect. Bushing for oil film bearings.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US07/487,287 | 1990-03-02 | ||
US07/487,287 US5000584A (en) | 1990-03-02 | 1990-03-02 | Bushing for oil film bearing |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH04331816A true JPH04331816A (en) | 1992-11-19 |
JP2501247B2 JP2501247B2 (en) | 1996-05-29 |
Family
ID=23935125
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP3021364A Expired - Lifetime JP2501247B2 (en) | 1990-03-02 | 1991-01-23 | Bushings for oil film bearings |
Country Status (10)
Country | Link |
---|---|
US (1) | US5000584A (en) |
EP (1) | EP0445472B1 (en) |
JP (1) | JP2501247B2 (en) |
CN (1) | CN1025361C (en) |
AT (1) | ATE102303T1 (en) |
BR (1) | BR9100450A (en) |
CA (1) | CA2032586C (en) |
DE (1) | DE69007079T2 (en) |
ES (1) | ES2049935T3 (en) |
MX (1) | MX165039B (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2014508257A (en) * | 2011-03-11 | 2014-04-03 | フエデラル―モーグル・ウイースバーデン・ゲゼルシヤフト・ミト・ベシユレンクテル・ハフツング | Plain bearing shell |
JP2014528841A (en) * | 2011-09-29 | 2014-10-30 | シーメンス インダストリー インコーポレイテッドSiemens Industry, Inc. | Lubricating system for hybrid hydrodynamic and hydrostatic bearing bushings and rolling mills |
JP2014237299A (en) * | 2013-06-10 | 2014-12-18 | ファナック株式会社 | Slide bearing of injection molding machine |
Families Citing this family (31)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5137418A (en) * | 1990-12-21 | 1992-08-11 | Roy E. Roth Company | Floating self-centering turbine impeller |
BR9100852A (en) * | 1991-02-25 | 1992-10-27 | Metal Leve Sa | SLIDING BEARING |
US5503478A (en) * | 1995-04-03 | 1996-04-02 | Federal-Mogul Corporation | Lubricant distribution system for bearings and bushings |
US5720558A (en) * | 1995-10-16 | 1998-02-24 | Dresser-Rand Company | Tilting bearing pad with an axial feed groove having an exit side profiled area |
EP0877866B2 (en) * | 1996-01-30 | 2004-09-01 | Federal-Mogul Wiesbaden GmbH & Co.KG | Sliding bearing element with lubricating oil pockets |
US6123461A (en) * | 1998-08-24 | 2000-09-26 | Morgan Construction Company | Oil film bearing sleeve and keying arrangement |
JP2002155946A (en) * | 2000-11-20 | 2002-05-31 | Daido Metal Co Ltd | Shaft support member |
TW515871B (en) * | 2001-08-21 | 2003-01-01 | Ind Tech Res Inst | Dynamic-static mixing pressure fluid bearings and method of manufacturing same |
US6604859B1 (en) * | 2002-01-23 | 2003-08-12 | Morgan Construction Company | Bushing for oil film bearing |
DE10336894A1 (en) * | 2003-08-08 | 2005-03-10 | Sms Demag Ag | Oil film bearing for roll neck with hydrostatic support |
US20050281499A1 (en) * | 2004-06-22 | 2005-12-22 | Wojtkowski Thomas Jr | Oil outlet for rolling mill oil film bearing |
KR100711444B1 (en) * | 2005-12-23 | 2007-04-24 | 주식회사 포스코 | Bearing device for zinc pot roll in continuous galvanizing line |
US7637895B2 (en) * | 2006-08-22 | 2009-12-29 | Nalin David R | System and device for medically treating an individual |
CN100464884C (en) * | 2006-12-07 | 2009-03-04 | 郑红专 | Self-lubricating segmental roller base |
US7708466B2 (en) * | 2007-05-21 | 2010-05-04 | Adda Corp. | Lubricated bushing |
DE102008054715A1 (en) * | 2008-12-16 | 2010-06-17 | Voith Patent Gmbh | Bearing for a rotatable and by vibration excitation in the direction of the axis of rotation movable roller, in particular breast roll and method for controlling the operation of such a roller |
ES2395350B1 (en) * | 2011-02-02 | 2014-09-09 | Fagor, S. Coop. | Mechanical press adapted to forming processes, in particular hot forming processes |
US20130004103A1 (en) * | 2011-06-30 | 2013-01-03 | Caterpillar, Inc. | Sleeve Bearing with Shell Portions of Unequal Extent |
DE102012208966A1 (en) * | 2012-05-29 | 2013-12-05 | Continental Automotive Gmbh | Exhaust gas turbocharger with floating bush bearing |
CN102854013B (en) * | 2012-08-22 | 2014-12-17 | 太原科技大学 | Comprehensive test device of oil film bearing |
EP2952757B1 (en) * | 2013-01-31 | 2020-03-11 | Mitsubishi Hitachi Power Systems, Ltd. | Tilting pad bearing device |
US9284976B2 (en) | 2013-03-09 | 2016-03-15 | Waukesha Bearings Corporation | Countershaft |
US9279446B2 (en) * | 2013-03-09 | 2016-03-08 | Waukesha Bearings Corporation | Bearing with axial variation |
CN105134781A (en) * | 2014-08-08 | 2015-12-09 | 摩尔动力(北京)技术股份有限公司 | Fluid directional suspension system |
US10006486B2 (en) * | 2015-03-05 | 2018-06-26 | Primetals Technologies USA LLC | Spherical oil film bearing |
DE102015209637A1 (en) * | 2015-05-26 | 2016-12-01 | Sms Group Gmbh | roll arrangement |
JP6529549B2 (en) * | 2017-07-31 | 2019-06-12 | 大同メタル工業株式会社 | Half bearing and slide bearing |
JP6577003B2 (en) * | 2017-11-17 | 2019-09-18 | 大同メタル工業株式会社 | Half bearing and plain bearing |
CN108571514B (en) * | 2018-06-25 | 2020-06-16 | 西安交通大学 | Semi-elliptical distribution textured surface for radial sliding bearing |
CN109458399A (en) * | 2019-01-11 | 2019-03-12 | 哈尔滨工程大学 | A kind of circumferential change wall thickness bearing shell |
US12018701B2 (en) * | 2020-09-24 | 2024-06-25 | Flowserve Pte. Ltd. | Hydraulic bearings and related devices, assemblies, and methods |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5481038U (en) * | 1977-11-18 | 1979-06-08 | ||
JPS54106443U (en) * | 1978-01-11 | 1979-07-26 | ||
JPS6240332U (en) * | 1985-08-30 | 1987-03-10 |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1746020A (en) * | 1928-05-02 | 1930-02-04 | Himself As Trustee | Bearing |
US3385009A (en) * | 1964-02-03 | 1968-05-28 | Landis Tool Co | Spindle bearings |
DE1450034A1 (en) * | 1964-05-02 | 1969-09-04 | Schmidt Gmbh Karl | Plain bearings with lubricant grooves |
FR1473978A (en) * | 1966-01-07 | 1967-03-24 | Cem Comp Electro Mec | Aerostatic gas bearing |
US3453031A (en) * | 1967-04-06 | 1969-07-01 | Morgan Construction Co | Bearing assembly |
NL7015119A (en) * | 1970-10-15 | 1972-04-18 | ||
DE2537046A1 (en) * | 1975-08-20 | 1977-03-03 | Schmidt Gmbh Karl | Hydrrddrrrodynnyynnnamic radial bearing pad rolled from plate - has lubrication groove to lessen cavitation and pitting |
US4159152A (en) * | 1977-10-11 | 1979-06-26 | Morgan Construction Company | Means for lubricating the roll neck/sleeve interface of an oil film bearing |
US4772137A (en) * | 1987-03-30 | 1988-09-20 | Morgan Construction Company | Oil film bearing and bushing |
DD271629A3 (en) * | 1987-11-23 | 1989-09-13 | Schwermasch Liebknecht Veb K | RADIAL BEARING |
-
1990
- 1990-03-02 US US07/487,287 patent/US5000584A/en not_active Expired - Lifetime
- 1990-12-18 CA CA002032586A patent/CA2032586C/en not_active Expired - Lifetime
- 1990-12-20 AT AT90314011T patent/ATE102303T1/en not_active IP Right Cessation
- 1990-12-20 DE DE69007079T patent/DE69007079T2/en not_active Expired - Lifetime
- 1990-12-20 ES ES90314011T patent/ES2049935T3/en not_active Expired - Lifetime
- 1990-12-20 EP EP90314011A patent/EP0445472B1/en not_active Expired - Lifetime
-
1991
- 1991-01-23 JP JP3021364A patent/JP2501247B2/en not_active Expired - Lifetime
- 1991-02-05 BR BR919100450A patent/BR9100450A/en not_active IP Right Cessation
- 1991-02-26 MX MX24695A patent/MX165039B/en unknown
- 1991-03-02 CN CN91101237A patent/CN1025361C/en not_active Expired - Lifetime
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5481038U (en) * | 1977-11-18 | 1979-06-08 | ||
JPS54106443U (en) * | 1978-01-11 | 1979-07-26 | ||
JPS6240332U (en) * | 1985-08-30 | 1987-03-10 |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2014508257A (en) * | 2011-03-11 | 2014-04-03 | フエデラル―モーグル・ウイースバーデン・ゲゼルシヤフト・ミト・ベシユレンクテル・ハフツング | Plain bearing shell |
JP2014528841A (en) * | 2011-09-29 | 2014-10-30 | シーメンス インダストリー インコーポレイテッドSiemens Industry, Inc. | Lubricating system for hybrid hydrodynamic and hydrostatic bearing bushings and rolling mills |
JP2014237299A (en) * | 2013-06-10 | 2014-12-18 | ファナック株式会社 | Slide bearing of injection molding machine |
Also Published As
Publication number | Publication date |
---|---|
CA2032586A1 (en) | 1991-09-03 |
EP0445472B1 (en) | 1994-03-02 |
ES2049935T3 (en) | 1994-05-01 |
MX165039B (en) | 1992-10-16 |
CN1054548A (en) | 1991-09-18 |
BR9100450A (en) | 1991-10-22 |
JP2501247B2 (en) | 1996-05-29 |
CA2032586C (en) | 1993-09-14 |
DE69007079D1 (en) | 1994-04-07 |
EP0445472A1 (en) | 1991-09-11 |
ATE102303T1 (en) | 1994-03-15 |
DE69007079T2 (en) | 1994-06-01 |
CN1025361C (en) | 1994-07-06 |
US5000584A (en) | 1991-03-19 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JPH04331816A (en) | Bush for oil film bearing | |
DE69921522T2 (en) | Gas-lubricated low-speed mechanical seal | |
US3891281A (en) | Pivoted pad bearing apparatus and method for bidirectional rotation | |
EP0792426B1 (en) | A shaft seal | |
US5133562A (en) | Drained face seal | |
JPH09503276A (en) | Face-sealing device with angled annular groove | |
US5871285A (en) | Hybrid combined hydrostatic and hydrodynamic bearing with enhanced stability and reduced flow rate | |
KR970011462A (en) | Fluid bearings for spindle motors with large inertia load | |
EP3653914A1 (en) | Sliding parts | |
US3622212A (en) | Hydrodynamic lubrication bearing | |
US5983781A (en) | Sliding bearing with self-adjusted load bearing capacity | |
US2731305A (en) | High speed thrust bearing structure | |
US4346947A (en) | Hydrostatic pressure gas-liquid double phase bearing | |
JPH10169609A (en) | Static pressure bearing for hydraulic servo cylinder | |
US4563137A (en) | Rotary hydraulic energy-conversion device with two dams engaging a rotatable ring | |
CN100532871C (en) | Variable curvature sliding bearing containing three oil wedges | |
JPH0261646B2 (en) | ||
US4624584A (en) | Sliding journal bearing | |
Prakash et al. | Theoretical effects of solid particles on the lubrication of journal bearings considering cavitation | |
JPS62101916A (en) | Improved bearing assembly and thrust bearing | |
JPS585135Y2 (en) | fluid sliding bearing | |
JPS6069318A (en) | Floating bush bearing | |
JPH11336753A (en) | Self-aligning roller bearing | |
JPS6322333Y2 (en) | ||
Razzaque et al. | Effects of the shape of surface micropores on the performance of a face seal |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20090313 Year of fee payment: 13 |
|
FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20090313 Year of fee payment: 13 |
|
FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20100313 Year of fee payment: 14 |
|
FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20100313 Year of fee payment: 14 |
|
FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20110313 Year of fee payment: 15 |
|
EXPY | Cancellation because of completion of term |